Swash plate for rotary compressor and rotary compressor

Abstract

This invention discloses a vane for a rotary compressor and a rotary compressor. The vane has a first end face and a second end face arranged opposite each other along the axial direction of the rotary compressor, and a first side face and a second side face arranged opposite each other along the radial direction of the rotary compressor. The first side face is located radially outside the second side face. At least one of the first end face and the second end face has a groove formed therein, the groove being spaced apart from the second side face, and the distance between the groove and the first side face is less than the distance between the groove and the second side face. The vane for a rotary compressor according to this invention facilitates the reduction of leakage at the axial end face, improves the energy efficiency of the rotary compressor, and simultaneously improves the lubrication effect of the vane.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a vane for a rotary compressor and a rotary compressor. Background Technology

[0002] In related technologies, the internal parts of the compressor are mostly fitted with clearances, which results in more leakage channels and a larger leakage volume, thus reducing the volumetric efficiency of the compressor and affecting its energy efficiency. Summary of the Invention

[0003] The present invention aims to at least solve one of the technical problems existing in the prior art. To this end, the present invention proposes a vane for a rotary compressor, which facilitates the reduction of leakage at the axial end face, improves the energy efficiency of the rotary compressor, and at the same time improves the lubrication effect of the vane.

[0004] The present invention also proposes a rotary compressor having the above-mentioned sliding vanes.

[0005] According to a first aspect embodiment of the present invention, a vane for a rotary compressor has a first end face and a second end face disposed opposite to each other along the axial direction of the rotary compressor, and a first side face and a second side face disposed opposite to each other along the radial direction of the rotary compressor. The first side face is located radially outside the second side face. At least one of the first end face and the second end face is formed with a groove. The groove is spaced apart from the second side face, and the distance between the groove and the first side face is less than the distance between the groove and the second side face. The maximum depth of the groove is M, where M≤0.5mm.

[0006] According to an embodiment of the present invention, a vane for a rotary compressor has a groove provided on at least one of a first end face and a second end face, such that the groove is spaced apart from the second side face, and the distance between the groove and the first side face is less than the distance between the groove and the second side face, and the maximum depth M of the groove is ≤0.5mm. This allows lubricating oil from the rotary compressor to flow into the groove, forming an oil film at the first end face and / or the second end face to achieve oil layer sealing. This effectively reduces the leakage of gas in the compression chamber at the first end face and / or the second end face, improves the energy efficiency of the rotary compressor, and simultaneously achieves lubrication of the first end face and / or the second end face, reducing the movement resistance of the vane and saving energy consumption of the rotary compressor.

[0007] In some embodiments, M further satisfies: M≤0.3mm.

[0008] In some embodiments, the radial length of the slide is L, the distance between the radial inner end of the groove and the second side surface is L1, L1-2*L2≥2mm, and L2 is the eccentricity of the rotary compressor; or, 0.3≤L1 / L≤0.6.

[0009] In some embodiments, the groove has a bottom wall and a side wall disposed at the radially inner end of the bottom wall, the side wall being inclined relative to the normal of the corresponding first end face or the normal of the second end face; and / or, the bottom wall forms an angle α with the corresponding first end face or the second end face, 1.5°≤α≤9°.

[0010] In some embodiments, the cross-sectional shape of the groove includes at least one of polygon, circle, semicircle, and ellipse.

[0011] In some embodiments, the width of the sliding vane in the circumferential direction of the rotary compressor is W, and the maximum width of the groove in the circumferential direction of the rotary compressor is W1, where 0.3 ≤ W1 / W ≤ 0.8.

[0012] In some embodiments, the groove extends through the first side surface; or, the groove and the first side surface are radially spaced apart along the rotary compressor.

[0013] In some embodiments, the first side has guide surfaces at its circumferential ends, and each guide surface extends from the inside out toward each other along the radial direction of the rotary compressor.

[0014] In some embodiments, the two guide surfaces are symmetrically arranged about the center surface of the vane, the center surface extending radially along the rotary compressor and perpendicular to the circumferential direction of the rotary compressor.

[0015] In some embodiments, the width of the guide surface in the circumferential direction of the rotary compressor is equal to the distance between the groove and the corresponding edge of the slide.

[0016] In some embodiments, the guide surface extends from the first end face to the second end face.

[0017] A rotary compressor according to a second aspect of the present invention includes vanes for a rotary compressor according to the first aspect of the present invention described above.

[0018] According to embodiments of the present invention, by employing the aforementioned sliding vanes, the leakage of the rotary compressor can be reduced, thereby facilitating the improvement of the volumetric efficiency and energy efficiency of the rotary compressor.

[0019] Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. Attached Figure Description

[0020] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the description of the embodiments taken in conjunction with the following drawings, in which:

[0021] Figure 1 This is a schematic diagram of a slider according to an embodiment of the present invention;

[0022] Figure 2 This is a schematic diagram of a slider according to another embodiment of the present invention;

[0023] Figure 3 This is a schematic diagram of the assembly of the sliding vane, cylinder, and piston according to an embodiment of the present invention;

[0024] Figure 4 This is a cross-sectional view of a rotary compressor according to an embodiment of the present invention.

[0025] Figure label:

[0026] Rotary compressor 100

[0027] Slider 1

[0028] First end face 1a, second end face 1b, first side face 1c, second side face 1d, guide face 1e

[0029] Groove 10, bottom wall 10a, side wall 10b

[0030] Cylinder 2, center hole 2a, slide groove 2b, spring hole 2c, tool relief groove 2d

[0031] Piston 3, housing 4, body 41, top cover 42, bottom cover 43

[0032] Drive assembly 5, motor 51, stator 511, rotor 512, drive shaft 52,

[0033] Main bearing 6, secondary bearing 7. Detailed Implementation

[0034] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0035] The following disclosure provides numerous different embodiments or examples for implementing various structures of the invention. To simplify the disclosure, specific examples of components and arrangements are described below. These are merely examples and are not intended to limit the invention. Furthermore, reference numerals and / or letters may be repeated in different examples. Such repetition is for simplification and clarity and does not in itself indicate a relationship between the various embodiments and / or arrangements discussed. Additionally, examples of various specific processes and materials are provided in this invention; however, those skilled in the art will recognize the applicability of other processes and / or the use of other materials.

[0036] Hereinafter, with reference to the accompanying drawings, a vane 1 for a rotary compressor 100 according to an embodiment of the present invention will be described.

[0037] like Figure 1 and Figure 2 As shown, the vane 1 has a first end face 1a, a second end face 1b, a first side face 1c, and a second side face 1d. The first end face 1a and the second end face 1b are arranged opposite each other along the axial direction of the rotary compressor 100, and the first side face 1c and the second side face 1d are arranged opposite each other along the radial direction of the rotary compressor 100. The first side face 1c is located on the radial outer side of the second side face 1d. Therefore, the end where the first side face 1c is located is the radial outer end of the vane 1, and the end where the second side face 1d is located is the radial inner end of the vane 1.

[0038] It should be noted that, in the description of this application, the direction "outside" refers to the direction away from the central axis of the rotary compressor 100 in the radial direction, and the opposite direction is defined as "inside"; wherein, the central axis of the rotary compressor 100 may refer to the central axis of the drive shaft 52 of the rotary compressor 100.

[0039] If at least one of the first end face 1a and the second end face 1b has a groove 10, then the following are some of the possible cases: 1. The first end face 1a has a groove 10, but the second end face 1b does not have a groove 10; 2. The second end face 1b has a groove 10, but the first end face 1a does not have a groove 10; 3. The first end face 1a and the second end face 1b each have a groove 10.

[0040] It is understandable that when the first end face 1a has a groove 10, the groove 10 of the first end face 1a can be formed by a portion of the first end face 1a recessing towards the second end face 1b; when the second end face 1b has a groove 10, the groove 10 of the second end face 1b can be formed by a portion of the second end face 1b recessing towards the first end face 1a.

[0041] Furthermore, when grooves 10 are formed on the first end face 1a and the second end face 1b respectively, the shape, size, and position of the groove 10 on the first end face 1a can be the same as or at least partially different from the shape, size, and position of the groove 10 on the second end face 1b. When the parameters of the groove 10 on the first end face 1a correspond to the parameters of the groove 10d on the second end face 1b, it facilitates the consistent design of the groove 10 on the first end face 1a and the groove 10 on the second end face 1b, which helps reduce design costs and simplifies the processing steps of the slider 1. The position of the groove 10 can be understood as the distance between the radially inner end of the groove 10 and the second side surface 1d. If the distance between the radially inner end of the groove 10 and the second side surface 1d is different, it indicates that the position of the groove 10 has changed.

[0042] Therefore, when the vane 1 is used in the rotary compressor 100, during the sliding process of the vane 1 in the vane groove 2b of the rotary compressor 100, the lubricating oil in the rotary compressor 100 can flow into the groove 10, so as to fill between the corresponding walls of the first end face 1a of the vane 1 and the vane groove 2b, and / or, fill between the corresponding walls of the second end face 1b of the vane 1 and the vane groove 2b, effectively improving the lubrication of the vane 1, reducing the movement resistance of the vane 1, and helping to save energy consumption of the rotary compressor 100; at the same time, the lubricating oil flowing into the groove 10 can also fill between the first end face 1a and / or the second end face 1b of the vane 1 and the corresponding walls of the vane groove 2b, effectively improving the lubrication of the vane 1, reducing the movement resistance of the vane 1, and helping to save energy consumption of the rotary compressor 100; at the same time, the lubricating oil flowing into the groove 10 can also fill between the first end face 1a and / or the second end face 1b. An oil film is formed on end face 1b to achieve oil layer sealing, thereby reducing gas leakage from the first end face 1a and / or the second end face 1b in the compression chamber of the rotary compressor 100, thereby improving the volumetric efficiency of the rotary compressor 100 and enhancing its energy efficiency. It also prevents high-pressure side gas outside the compression chamber from entering the low-pressure side of the compression chamber from the first end face 1a and / or the second end face 1b, and prevents high-pressure side gas inside the compression chamber from entering the low-pressure side of the compression chamber from the first end face 1a and / or the second end face 1b, effectively ensuring the working efficiency of the rotary compressor 100.

[0043] It should be noted that, in the description of this application, "and / or" means that there are three parallel options. Taking "A and / or B" as an example, it includes option A, option B, or an option that satisfies both A and B.

[0044] like Figures 1-3As shown, the groove 10 is spaced apart from the second side 1d, and the distance between the groove 10 and the first side 1c is less than the distance between the groove 10 and the second side 1d. Therefore, relative to the second side 1d, the groove 10 is located adjacent to the first side 1c. Thus, when the vane 1 is used in the rotary compressor 100, since the second side 1d is located inside the compression chamber of the rotary compressor 100, the groove 10 is always located outside the compression chamber during the sliding process of the vane 1. Therefore, the gas in the compression chamber will not exert pressure on the lubricating oil in the groove 10, so as to ensure the oil sealing effect at the first end face 1a and / or the second end face 1b.

[0045] The distance between the groove 10 and the first side 1c can be understood as the radial distance between the end of the groove 10 adjacent to the first side 1c and the first side 1c, and this distance can be greater than or equal to 0; the distance between the groove 10 and the second side 1d can be understood as the radial distance between the end of the groove 10 adjacent to the second side 1d and the second side 1d, and this distance is greater than 0.

[0046] Therefore, according to the embodiments of the present invention, the vane 1 of the rotary compressor 100, by providing a groove 10 on at least one of the first end face 1a and the second end face 1b, and such that the groove 10 is spaced apart from the second side face 1d, and the distance between the groove 10 and the first side face 1c is less than the distance between the groove 10 and the second side face 1d, the lubricating oil of the rotary compressor 100 can flow into the groove 10 to form an oil film at the first end face 1a and / or the second end face 1b to achieve oil layer sealing, effectively reducing the leakage of gas in the compression chamber at the first end face 1a and / or the second end face 1b, improving the energy efficiency of the rotary compressor 100, and simultaneously achieving lubrication of the first end face 1a and / or the second end face 1b, reducing the movement resistance of the vane 1, and saving energy consumption of the rotary compressor 100.

[0047] In some embodiments of the present invention, the maximum depth of the groove 10 is M. When the groove 10 is a groove of uniform depth, the depth corresponding to any position of the groove 10 is equal, and the maximum depth of the groove 10 is the depth corresponding to any position within the groove 10. When the groove 10 is a groove of unequal depth, the maximum depth of the groove 10 can be understood as the maximum value among the depths corresponding to all positions of the groove 10. Wherein, M ≤ 0.5mm, for example, M can be 0.2mm, or 0.35mm, or 0.4mm, or 0.46mm, or 0.5mm, etc., so as to ensure that the oil layer at the first end face 1a and / or the second end face 1b has a suitable thickness to ensure the oil sealing effect of the oil layer, and to avoid the groove 10 being too deep, which would prevent the formation of a sealing oil layer or prevent the oil film from having sufficient pressure.

[0048] In some embodiments of the present invention, M further satisfies M≤0.3mm, for example, M can be 0.3mm, or 0.25mm, or 0.2mm, or 0.18mm, etc., so as to ensure the oil sealing effect at the first end face 1a and / or the second end face 1b while ensuring the lubrication effect at the first end face 1a and / or the second end face 1b.

[0049] In some embodiments of the present invention, such as Figure 3 As shown, the radial length of the vane 1 is L, that is, the length of the vane 1 in the radial direction of the compressor is L. The distance between the radial inner end of the groove 10 and the second side 1d is L1, L1-2*L2≥2mm, and L2 is the eccentricity of the rotary compressor 100. When the vane 1 is used in the rotary compressor 100, the vane 1 has a first extreme sliding position and a second extreme sliding position. The vane 1 slides between the first extreme sliding position and the second extreme sliding position. In the first extreme sliding position, the radial distance between the second side 1d of the vane 1 and the central axis of the compression chamber is the largest. At this time, the radial length of the part of the vane 1 that extends into the compression chamber is the shortest. In the second extreme sliding position (e.g. Figure 3 As shown), the radial distance between the second side 1d of the slider 1 and the central axis of the compression cavity is the smallest. At this time, the radial length of the part of the slider 1 extending into the compression cavity is the longest. Therefore, L1-2*L2 can be understood as the radial distance between the radial inner end of the groove 10 and the peripheral wall of the compression cavity when the slider 1 is in the second extreme position. Figure 3 H = L1-2*L2≥2mm, to ensure that the groove 10 is always separated from the compression chamber during the sliding process of the vane 1, so that the first end face 1a and / or the second end face 1b of the vane 1 can be sealed, preventing the gas in the compression chamber, especially the gas on the high pressure side, from leaking through the groove 10, thereby further ensuring the volumetric efficiency of the rotary compressor 100.

[0050] The distance L1 between the radial inner end of the groove 10 and the second side surface 1d can be understood as the distance between the radial inner edge of the groove 10 and the second side surface 1d in the radial direction of the rotary compressor 100. For example, the radial inner edge of the groove 10 can be understood as the edge of the side wall 10b of the groove 10 away from the bottom wall 10a, as described below.

[0051] Of course, this application is not limited to this; in other embodiments, L and L1 can also satisfy: 0.3≤L1 / L≤0.6, for example, L1 can be 0.3L, or 0.45L, or 0.5L, or 0.52L, or 0.6L, etc.; it can be seen that at this time, the setting position of the groove 10 can be reasonably adjusted by setting the proportion of the distance between the radial inner end of the groove 10 and the second side 1d to the length of the entire slide plate 1, which also makes it easy to ensure that the groove 10 is always located outside the compression cavity and will not communicate with the compression cavity during the entire sliding process of the slide plate 1. Further, 0.4≤L1 / L≤0.7.

[0052] In some embodiments of the present invention, such as Figure 1 and Figure 2 As shown, the groove 10 has a bottom wall 10a and a side wall 10b with a radially inner end of the bottom wall 10a. The side wall 10b is inclined relative to the normal of the corresponding first end face 1a or the normal of the second end face 1b. That is, when the groove 10 is a groove 10 on the first end face 1a, the side wall 10b of the groove 10 is inclined relative to the normal of the first end face 1a. When the groove 10 is a groove 10 on the second end face 1b, the side wall 10b of the groove 10 is inclined relative to the normal of the second end face 1b. This makes it easier for a portion of the lubricating oil in the groove 10 corresponding to the side wall 10b to form a wedge-shaped oil film. This facilitates the rapid filling of the entire groove 10 by the lubricating oil. At the same time, the oil film pressure of the wedge-shaped oil film is higher, which can further improve the oil layer sealing effect and reduce the leakage at the first end face 1a and / or the second end face 1b.

[0053] Optionally, the inclination angle of the sidewall 10b relative to the normal of the corresponding first end face 1a or the normal of the second end face 1b is 20° to 60°; but it is not limited to this.

[0054] Of course, this application is not limited to this; in other embodiments, the bottom wall 10a forms an angle α with the corresponding first end face 1a or second end face 1b. That is, when the groove 10 is a groove 10 on the first end face 1a, the bottom wall 10a of the groove 10 forms an angle α with the first end face 1a; when the groove 10 is a groove 10 on the second end face 1b, the bottom wall 10a of the groove 10 forms an angle α with the second end face 1b. Wherein, 1.5°≤α≤9°, that is, the bottom wall 10a is inclined relative to the corresponding first end face 1a or second end face 1b, which also facilitates the formation of a wedge-shaped oil film by the portion of lubricating oil in the groove 10 corresponding to the bottom wall 10a, which facilitates the rapid filling of the entire groove by the lubricating oil. At the same time, the oil film pressure of the wedge-shaped oil film is higher, so as to further improve the oil layer sealing effect.

[0055] In some other embodiments, the sidewall 10b is inclined relative to the normal of the corresponding first end face 1a or the normal of the second end face 1b, and the bottom wall 10a forms an angle α with the corresponding first end face 1a or the second end face 1b, where 1.5°≤α≤9°, to ensure that a wedge-shaped oil film is formed in the entire groove 10, thereby further improving the oil layer sealing effect.

[0056] Optionally, both the bottom wall 10a and the side wall 10b are formed as planes to facilitate the machining and forming of the groove 10.

[0057] In some embodiments of the present invention, such as Figure 1 and Figure 2 As shown, the cross-sectional shape of the groove 10 includes at least one of polygons (e.g., triangles, quadrilaterals such as rectangles, trapezoids, etc.), circles, semicircles, and ellipses, which can include the following cases: 1. The cross-sectional shape of the groove 10 is a polygon (e.g., Figure 1 and Figure 2 1. The cross-sectional shape of the groove 10 is rectangular; 2. The cross-sectional shape of the groove 10 is circular; 3. The cross-sectional shape of the groove 10 is semi-circular; 4. The cross-sectional shape of the groove 10 is elliptical; 5. The cross-sectional shape of the groove 10 is a combination of at least two of the following: polygonal, circular, semi-circular, and elliptical. Therefore, the shape of the groove 10 is flexible and can easily adapt to the differentiated needs of different rotary compressors 100.

[0058] For example, the cross-sectional shape of the groove 10 can be a combination of a rectangle and a semicircle, with the semicircle located at the radial inner end of the rectangle.

[0059] It should be noted that the cross-section of the groove 10 is perpendicular to the axial direction of the rotary compressor 100. Of course, the cross-sectional shape of the groove 10 can also be formed in other shapes, and is not limited to this.

[0060] In some embodiments of the present invention, the width of the vane 1 in the circumferential direction of the rotary compressor 100 is W, and the maximum width of the groove 10 in the circumferential direction of the rotary compressor 100 is W1, 0.3≤W1 / W≤0.8. For example, W1 can be equal to 0.3W, or 0.4W, or 0.5W, or 0.7W, or 0.8W, etc. It can be seen that in the circumferential direction of the rotary compressor 100, it is easy to ensure that the groove 10 does not penetrate the circumferential side surfaces of the vane 1, and it is easy to make the groove 10 define a space with a certain degree of sealing, which is beneficial to ensure the film pressure of the oil layer in the groove 10 and further ensure the oil sealing effect.

[0061] It is understandable that the groove 10 can be formed as a groove of equal width in the circumferential direction of the rotary compressor 100. In this case, the maximum width W1 of the groove 10 in the circumferential direction of the rotary compressor 100 can be the width at any position of the groove 10. The groove 10 can also be formed as a groove of non-equal width in the circumferential direction of the rotary compressor 100. The maximum width W1 of the groove 10 can be understood as the maximum value among the widths corresponding to all positions of the groove 10.

[0062] Optionally, when the groove 10 is a non-uniform width groove, the width of the groove 10 can gradually increase from the inside to the outside along the radial direction of the rotary compressor 100.

[0063] Furthermore, 0.4≤W1 / W≤0.7 is beneficial for further improving the oil seal effect.

[0064] In some embodiments of the present invention, such as Figure 2 As shown, the groove 10 penetrates the first side surface 1c. At this time, the distance between the groove 10 and the first side surface 1c can be 0. In this case, there is no need to consider the specific distance between the groove 10 and the first side surface 1c, which helps to reduce design costs.

[0065] Of course, this application is not limited to this; in other embodiments, such as Figure 1 As shown, the groove 10 and the first side surface 1c are arranged radially apart along the rotary compressor 100. At this time, the distance between the groove 10 and the first side surface 1c can be greater than 0. That is, the groove 10 does not penetrate the first side surface 1c, which helps to ensure the pressure of the oil film in the groove 10.

[0066] In some embodiments of the present invention, such as Figure 1 and Figure 2 As shown, the first side surface 1c has guide surfaces 1e at both circumferential ends. One circumferential end of the first side surface 1c has a guide surface 1e, and the other circumferential end of the first side surface 1c also has a guide surface 1e. Along the radial direction of the rotary compressor 100, each guide surface 1e extends from the inside out toward each other, so that the cross-sectional area of ​​the portion of the vane 1 with the guide surface 1e at the end corresponding to the first side surface 1c gradually decreases from the inside out in the radial direction of the rotary compressor 100. Thus, when the vane 1 moves from the inside out, the guide surface 1e can squeeze the lubricating oil on the radially outer side of the vane 1 to the circumferential sides of the vane 1, so as to increase the amount of lubricating oil between the circumferential sides of the vane 1 and the vane groove 2b, improve the lubrication effect on the circumferential sides of the vane 1, and at the same time, it is easier to reduce the motion resistance exerted by the lubricating oil on the radially outer side of the vane 1 on the vane 1, which is beneficial to further reduce the energy consumption of the rotary compressor 100.

[0067] It is understandable that when the vane 1 is applied in the rotary compressor 100, when there is sufficient lubricating oil in the rotary compressor 100, at least a part of the vane 1 will be immersed in the lubricating oil. For example, when the rotary compressor 100 is set vertically, the lower part or the entire vane 1 is immersed in the lubricating oil. During the movement of the vane 1, especially when the vane 1 moves from the inside to the outside, the lubricating oil will exert a large resistance to the movement of the vane 1. However, by providing guide surfaces 1e at both ends of the first side 1c in the circumferential direction, this application can effectively reduce the resistance of the lubricating oil to the vane 1, improve the smoothness of the movement of the vane 1, and help reduce the energy consumption of the rotary compressor 100.

[0068] Optionally, the guide surface 1e can be a plane or a smooth curved surface, which helps to ensure the smoothness of the guide surface 1e and further reduce the resistance of the lubricating oil to the movement of the slide 1.

[0069] Optionally, the shapes of the guide surfaces 1e at both ends of the first side surface 1c in the circumferential direction can be the same or different; for example, the guide surface 1e at one end of the first side surface 1c in the circumferential direction is a plane, and the guide surface 1e at the other end of the first side surface 1c in the circumferential direction is a curved surface, such as a circular arc surface, an elliptical arc surface, etc.; or, the guide surfaces 1e at both ends of the first side surface 1c in the circumferential direction are both planes; or, the guide surfaces 1e at both ends of the first side surface 1c in the circumferential direction are both curved surfaces.

[0070] It is understandable that, in the circumferential direction of the rotary compressor 100, the sum of the widths of the two guide surfaces 1e can be less than or equal to the width of the entire vane 1.

[0071] In some embodiments of the present invention, such as Figure 1 and Figure 2 As shown, the two guide surfaces 1e are symmetrically arranged about the center surface of the slide vane 1. The center surface extends radially along the rotary compressor 100 and is perpendicular to the circumference of the rotary compressor 100. Therefore, the center surface can be understood as the width center surface of the slide vane 1. Thus, during the movement of the slide vane 1 from the inside to the outside, the force exerted by the lubricating oil on the slide vane 1 through the guide surfaces 1e is relatively even in the circumferential direction of the slide vane 1, which facilitates the improvement of the smoothness and stability of the slide vane 1's sliding.

[0072] In some embodiments of the present invention, such as Figure 1 and Figure 2As shown, the width of the guide surface 1e in the circumferential direction of the rotary compressor 100 is equal to the distance between the corresponding edges of the groove 10 and the vane 1. Therefore, in the circumferential direction of the rotary compressor 100, the width of the groove 10 is less than the width of the vane 1. The edges of the groove 10 on both sides in the circumferential direction are spaced apart from the corresponding edges of the vane 1 on both sides in the circumferential direction. At the same time, the sum of the widths of the two guide surfaces 1e is less than the width of the entire vane 1. This makes it easier to ensure that the guide surface 1e only guides part of the lubricating oil to the circumferential sides of the vane 1, while the other part of the lubricating oil opposite to the groove 10 can flow into the groove 10 to ensure the formation of the oil layer in the groove 10.

[0073] Optionally, in Figure 1 and Figure 2 In the example, the widths of the two guide surfaces 1e are equal.

[0074] In some embodiments of the present invention, such as Figure 1 and Figure 2 As shown, the guide surface 1e extends from the first end face 1a to the second end face 1b. That is, one axial end of the guide surface 1e is flush with the first end face 1a, and the other axial end of the guide surface 1e is flush with the second end face 1b. This facilitates the effective reduction of the resistance applied by the lubricating oil to the entire slide vane 1, and at the same time helps to ensure that the entire slide vane 1 is subjected to a more balanced force in the axial direction of the rotary compressor 100, so as to further improve the smoothness and stability of the slide vane 1.

[0075] A rotary compressor 100 according to a second aspect embodiment of the present invention includes a vane 1 for a rotary compressor 100 according to the first aspect embodiment described above.

[0076] According to an embodiment of the present invention, by employing the aforementioned vane 1, the leakage of the rotary compressor 100 can be reduced, thereby improving the volumetric efficiency and energy efficiency of the rotary compressor 100.

[0077] The inventors of this application, through research, discovered that in the rotary compressor 100, the leakage through the radial gap between components is the largest, accounting for approximately 50% of the total leakage, followed by leakage through the axial end face gap of the suction chamber, which accounts for approximately 20% of the total leakage. Therefore, this application provides a groove 10 on at least one of the first end face 1a and the second end face 1b of the vane 1, so that lubricating oil can flow into the groove 10 during the operation of the vane 1, forming an oil film at the first end face 1a and / or the second end face 1b, thereby achieving oil layer sealing at the first end face 1a and / or the second end face 1b, reducing the leakage at the first end face 1a and / or the second end face 1b of the vane 1, and further reducing the leakage of the moving pair between the vane 1 and the vane groove 2b, improving the volumetric efficiency of the rotary compressor 100, and thus improving the energy efficiency of the rotary compressor 100.

[0078] It is understood that the rotary compressor 100 of this application can be applied to refrigerant circulation systems, such as air conditioners, refrigerators, heat pump systems, etc. When the rotary compressor 100 is applied to an air conditioner, it helps to reduce the energy consumption of the air conditioner, achieve the goal of energy saving and emission reduction, and thus facilitate the high-efficiency design of the air conditioner.

[0079] For example, in Figure 3 and Figure 4 In the example, the rotary compressor 100 also includes a cylinder 2 and a piston 3. A central hole 2a and a vane groove 2b are formed on the cylinder 2. The central hole 2a extends through the cylinder 2 along the axial direction of the cylinder 2 and helps to define the compression chamber of the rotary compressor 100. The vane groove 2b is formed on the peripheral wall of the central hole 2a. The vane groove 2b can extend radially or substantially radially along the cylinder 2 and communicates with the central hole 2a. The piston 3 is eccentrically disposed in the central hole 2a and can roll along the peripheral wall of the central hole 2a.

[0080] In this design, the slider 1 is slidably fitted into the slider groove 2b, at least a portion of the slider 1 is disposed within the slider groove 2b, and the slider 1 can reciprocate along the radial direction from the slider groove 2b. The two ends of the slider 1 along the sliding direction are the inner end and the outer end of the slider 1, respectively. The inner end of the slider 1 is the end of the slider 1 closer to the center of the central hole 2a, and the outer end of the slider 1 is the end of the slider 1 farther from the center of the central hole 2a. Thus, the inner end of the slider 1 corresponds to the second side surface 1d, and the outer end of the slider 1 corresponds to the first side surface 1c. During the reciprocating sliding process of the slider 1 along the slider groove 2b, at some times, the inner end of the slider 1 can extend into the central hole 2a through the slider groove 2b, and at some times, the outer end of the slider 1 can extend into the tool relief groove 2d disposed on the radial outer side of the slider groove 2b through the slider groove 2b. The tool relief groove 2d penetrates the cylinder 2 along the axial direction of the cylinder 2.

[0081] exist Figure 4 In the example, the rotary compressor 100 is a vertical compressor, and the first end face 1a and the second end face 1b can be the upper end face and the lower end face of the vane 1, respectively.

[0082] The cylinder 2 may also have a spring hole 2c. The spring hole 2c extends radially or generally radially along the cylinder 2. One end of the spring hole 2c extends to penetrate the outer circumferential surface of the cylinder 2, and the other end of the spring hole 2c extends to communicate with the vane groove 2b. A spring is provided in the spring hole 2c. The spring abuts against the outer end of the vane 1 to support the inner end of the vane 1 to extend into the central hole 2a through the vane groove 2b and abut against the outer circumferential surface of the piston 3, so that the inner end of the vane 1 always abuts against the outer circumferential wall of the piston 3. The vane 1 and the piston 3 cooperate to divide the central hole 2a into an intake chamber and an exhaust chamber located on both sides of the vane 1. As the piston 3 rotates and with the support of the spring, the vane 1 is pushed to slide along the vane groove 2b, thereby realizing the change in the volume of the intake chamber and the exhaust chamber, and realizing the intake, compression and exhaust work of the rotary compressor 100.

[0083] It is understandable that the cylinder 2 can have an intake port and an exhaust port, which are respectively located on both sides of the vane groove 2b. The intake port is connected to the intake chamber, and the exhaust port is connected to the exhaust chamber. During the rotation of the piston 3, as the volume of the intake chamber gradually increases, the intake chamber can draw in refrigerant through the intake port, while the volume of the exhaust chamber gradually decreases to compress the refrigerant in the exhaust chamber and exhaust it through the exhaust port.

[0084] Taking a single-cylinder rotary compressor 100 as an example, in... Figure 4 In the example, the cylinder 2 has a main bearing 6 and a secondary bearing 7 at its axial ends, respectively. The main bearing 6 and the secondary bearing 7 respectively close the axial ends of the central hole 2a, thus defining the compression chamber together with the cylinder 2. The slide vane 1 and the piston 3 cooperate to divide the compression chamber into an intake chamber and an exhaust chamber. The main bearing 6 may have an opening opposite to the relief groove 2d, which communicates with the relief groove 2d. Some lubricating oil can flow through this opening, and / or the gap between the main bearing 6 and the housing 4 of the rotary compressor 100, to the slide vane 1, flowing into the groove 10 of the slide vane 1 to form an oil layer. Of course, the rotary compressor 100 can also be a twin-cylinder rotary compressor 100, etc.

[0085] like Figure 4 As shown, the rotary compressor 100 also includes a housing 4 and a drive assembly 5. The drive assembly 5 is disposed inside the housing 4 and is connected to the piston 3 to drive the piston 3 to rotate eccentrically relative to the cylinder 2 within the cylinder 2. The drive assembly 5 may include a motor 51 and a drive shaft 52. The motor 51 may be an internal rotor motor or an external rotor motor. The motor 51 includes a stator 511 and a rotor 512. The stator 511 is fixed to the housing 4, and the rotor 512 is connected to the drive shaft 52 so that when the motor 51 is working, the rotor 512 drives the drive shaft 52 to rotate. The drive shaft 52 has an eccentric part, and the piston 3 is sleeved on the eccentric part so that when the drive shaft 52 rotates, the piston 3 can roll along the wall of the central hole 2a of the cylinder 2.

[0086] The housing 4 may include a body 41, an upper cover 42 and a bottom cover 43. The upper cover 42 and the bottom cover 43 are respectively located at the two ends of the axial direction of the body 41. When the rotary compressor 100 is vertically installed, the bottom cover 43 is located at the bottom of the body 41 and can help define the oil reservoir of the rotary compressor 100.

[0087] Other configurations and operations of the rotary compressor 100 according to embodiments of the present invention are known to those skilled in the art and will not be described in detail here.

[0088] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential," etc., indicating orientation or positional relationships, are based on the orientation or positional relationships shown in the accompanying drawings and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. Furthermore, features defined with "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0089] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0090] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "illustrative embodiment," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples.

[0091] Although embodiments of the invention have been shown and described, those skilled in the art will understand that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the invention, the scope of which is defined by the claims and their equivalents.

Claims

1. A sliding vane for a rotary compressor, characterized in that, The vane has a first end face and a second end face that are arranged opposite each other along the axial direction of the rotary compressor, and a first side face and a second side face that are arranged opposite each other along the radial direction of the rotary compressor. The first side face is located radially outside the second side face. At least one of the first end face and the second end face is formed with a groove. The groove is spaced apart from the second side face, and the distance between the groove and the first side face is less than the distance between the groove and the second side face. The radial length of the slider is L, and the distance between the radial inner end of the groove and the second side surface is L1. L1-2*L2≥2mm, where L2 is the eccentricity of the rotary compressor; or, 0.3≤L1 / L≤0.6; The groove has a bottom wall and a side wall located at the radially inner end of the bottom wall. The sidewall is inclined relative to the normal of the corresponding first end face or the normal of the second end face; and / or The bottom wall forms an angle α with the corresponding first end face or second end face, where 1.5°≤α≤9°; The maximum depth of the groove is M, where M ≤ 0.3 mm; The width of the sliding vane in the circumferential direction of the rotary compressor is W, and the maximum width of the groove in the circumferential direction of the rotary compressor is W1, where 0.3 ≤ W1 / W ≤ 0.

8. The first side has guide surfaces at both circumferential ends, and each guide surface extends from the inside out toward each other along the radial direction of the rotary compressor. The width of the guide surface in the circumferential direction of the rotary compressor is equal to the distance between the groove and the corresponding edge of the slide.

2. The vane for a rotary compressor according to claim 1, characterized in that, The cross-sectional shape of the groove includes at least one of polygon, circle, semicircle, and ellipse.

3. The vane for a rotary compressor according to claim 1, characterized in that, The groove extends through the first side surface; or, the groove and the first side surface are arranged radially apart along the rotary compressor.

4. The vane for a rotary compressor according to claim 1, characterized in that, The two guide surfaces are symmetrically arranged about the center surface of the vane, which extends radially along the rotary compressor and is perpendicular to the circumference of the rotary compressor.

5. The vane for a rotary compressor according to claim 1, characterized in that, The guide surface extends from the first end face to the second end face.

6. A rotary compressor, characterized in that, Includes a vane for a rotary compressor according to any one of claims 1-5.

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